EP1003980A1 - Cylindre pour matiere de type bande pouvant etre cintre - Google Patents

Cylindre pour matiere de type bande pouvant etre cintre

Info

Publication number
EP1003980A1
EP1003980A1 EP98938719A EP98938719A EP1003980A1 EP 1003980 A1 EP1003980 A1 EP 1003980A1 EP 98938719 A EP98938719 A EP 98938719A EP 98938719 A EP98938719 A EP 98938719A EP 1003980 A1 EP1003980 A1 EP 1003980A1
Authority
EP
European Patent Office
Prior art keywords
roll
axle journal
support sleeve
fastening
attached
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP98938719A
Other languages
German (de)
English (en)
Other versions
EP1003980B1 (fr
Inventor
Juha ISOMETSÄ
Tuomo Kurkela
Jorma Snellman
Pekka Kivioja
Mauri RUKAJÄRVI
Esa Vilmusenaho
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valmet Technologies Oy
Original Assignee
Valmet Oy
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from FI973388A external-priority patent/FI102560B1/fi
Application filed by Valmet Oy filed Critical Valmet Oy
Publication of EP1003980A1 publication Critical patent/EP1003980A1/fr
Application granted granted Critical
Publication of EP1003980B1 publication Critical patent/EP1003980B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—Bearings
    • F16C13/022—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle
    • F16C13/024—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H27/00—Special constructions, e.g. surface features, of feed or guide rollers for webs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—Bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/10—Rollers
    • B65H2404/13—Details of longitudinal profile
    • B65H2404/137—Means for varying longitudinal profiles
    • B65H2404/1371—Means for bending, e.g. for controlled deflection

Definitions

  • the invention concerns a roll that can be bent for a web-like material as defined in the preamble of claim 1.
  • rolls that can be bent have been formed so that they have a con- tinuous axle and a roll mantle composed of a number of parts fitted on the axle.
  • the roll can be curved in the desired shape by shifting the outermost journalling points of the roll mantle in the radial direction, in which case the mantle forms an arc or a broken line.
  • the parts of the mantle have, as a rule, been mounted on the axle each of them separately, in which case the arrangement comprises a number of bearings.
  • the conventional solutions often involve problems, which include, among other things, bearing problems in the roll and heat peaks produced by the bearings in the paper web.
  • a roll mantle composed of a number of parts may also form a considerable problem, because the gaps between the parts may mark the paper web and because the shape of the arc of the roll is not optimal, but the shape line of the roll is shaped as a broken line. Further, owing to the metallic roll mantle, problems of corrosion may arise.
  • the roll described in the applicant's FI Utility Model No. 2788 comprises a non- revolving roll axle and a roll mantle mounted on the axle revolving by means of bearings.
  • the roll mantle is a continuous tubular mantle, and the roll axle consists of three parts linked with each other.
  • support sleeves have been fitted, onto which sleeves the roll mantle itself has been mounted.
  • the roll mantle has been mounted on each of the end parts of the axle by the intermediate of said support sleeves by means of two bearings placed at an axial distance from one another.
  • the end parts of the axle have been connected with the middle part of the axle by means of articulated members so that the end parts of the axle can be inclined in relation to the middle part of the axle.
  • the inclining takes place so that the end parts of the axle move in relation to the middle part of the axle in the radial direction.
  • the roll bending mechanism comprises a cam member which forms a lever with two arms and which has been mounted pivotally on the wall of the tubular end part.
  • the inner end of the cam member extends through the wall of said tubular end part to outside the end part and is supported against the inner face of the middle part.
  • an axially displaceable regulation rod has been fitted, whose inner end is supported against the cam mem- ber.
  • the cam member When the cam member is shifted in the axial direction, the cam member can be pivoted so that it is supported with a greater force against the inner face of the middle part of the axle while, at the same time, increasing the distance between the end part and the middle part of the axle at the side of the cam member, in which case the axle is bent.
  • the roll mantle can be made of steel or of a composite material.
  • the roll described in the applicant's FI Patent Application No. 970379 is composed of two end parts and of a middle part.
  • the roll has no separate axle with a mantle revolving on said axle, but the middle part also operates as the axle of the roll, which is mounted on its support members by means of end bearings.
  • the extensions of the middle part which operates as the axle have diameters substantially smaller than the diameter of the middle part, and their size corresponds to the diameter of an ordinary non-revolving axle.
  • the end parts of the roll are tubular pieces, and they have been mounted directly on extensions of the middle part so that, at the inner ends of the end parts, articulation means have been fitted in the interior of the tubular end parts.
  • the tubular end parts have been supported in the axial direction, in the area of their outer ends, by means of bearings, which have been fitted on support parts separate from the revolving parts.
  • the support parts comprise sleeve-like pieces, whose inner diameter is larger that the diameter of the extension of the middle part, so that the positions of the bearings can be regulated radially.
  • a roll is described that is provided with a continuous roll mantle or with a roll mantle composed of a number of parts.
  • the material of the roll mantle is reinforced plastic or a similar composite construction.
  • the roll is provided with a continuous support axle extending across the whole roll mantle, which axle is not rotated and which is supported in its place. In the middle portion of the support axle there is a thicker portion, on which the middle bearings of the roll have been mounted. Said bearings are supported on annular fitting pieces, by whose means the outer race of the bearing is supported on the roll mantle.
  • sleeves At the ends of the roll, sleeves have been installed so that the sleeves extend a certain distance into the interior of the roll mantle and a certain distance to outside the roll mantle.
  • the ends of the roll mantle have been journalled on said sleeves.
  • a continuous support axle is used which extends through the whole roll mantle and in whose middle part there is a thicker portion.
  • the roll becomes relatively expensive and heavy.
  • the roll has bearings also in the middle portion of the roll at the thicker portion of the support axle.
  • a roll made of a composite material has been described.
  • the invention of said EP patent application concerns the structures and materials of different surface layers of the roll mantle.
  • Fig. 4 illustrates a revolving roll manufactured in accordance with the invention and meant for very high speeds, which roll is provided with a roll mantle of a composite material and with axle journals at the ends of the roll mantle. The axle journals are connected with the roll mantle by means of end flanges.
  • Said EP patent application is expressly concerned with the material structure of the roll mantle, the object being to manufacture a roll of sufficient surface hardness, low weight, and high dimensional preci- sion. The application does not mention bending of the roll.
  • a composite roll Owing to the favourable material properties of a composite roll, such as modulus of elasticity and density, a composite roll can be dimensioned so that it can be bent to the desired curve form with a reasonable torque and that it operates either at a speed below the critical speed, i.e. below the lowest resonance frequency, or between resonance frequencies. If a steel roll is supposed to be bent to a required curve form without increasing the strains excessively, the roll diameter must be very small. In such a case, one or several critical speeds of the roll must be surpassed unavoidably.
  • the roll in accordance with the present invention there is a continuous tubular roll mantle of a composite material. At both ends of the roll mantle there are axle journals, by whose means the roll is attached to the frame of the machine. Thus, the roll has no axle passing through the roll at all.
  • the construction of the roll in accordance with the present invention is clearly simpler, and its need of maintenance is little.
  • the simple construction makes the manufacture of the roll easy and of low cost. Also, the simple construction facilitates servicing of the roll.
  • Figure 1 is a schematic illustration of principle, in which a continuous tubular roll mantle is bent by means of a torque applied to both ends of the roll mantle.
  • FIG. 2 is a schematic illustration of an embodiment of the roll in accordance with the invention in which the bearings are fitted in the interior of the roll mantle and in which the bending mechanism is a screw member.
  • Figure 3 shows a variation of the embodiment shown in Fig. 2.
  • Figure 4 shows a second variation of the embodiment shown in Fig. 2.
  • Figure 5 shows a third variation of the embodiment shown in Fig. 2.
  • Figure 6 shows a fourth variation of the embodiment shown in Fig. 2.
  • FIG. 7 is a schematic illustration of an embodiment of the roll in accordance with the invention in which the bearings are fitted outside the roll mantle and the bending mechanism is a screw member.
  • Figure 8 shows a variation of the embodiment shown in Fig. 7.
  • Figure 9 shows a second variation of the embodiment shown in Fig. 7.
  • Figure 10 is a schematic illustration of an embodiment of the roll in accordance with the invention, in which the bearings are fitted outside the roll mantle and the bending of the roll is carried out in two planes.
  • Figure 11 shows a variation of the embodiment shown in Fig. 10.
  • Figure 12 shows a second variation of the embodiment shown in Fig. 10.
  • Figure 13 shows a third variation of the embodiment shown in Fig. 10.
  • Figure 14 is a schematic illustration of an embodiment of the roll in accordance with the invention, in which the bearings are fitted outside the roll mantle and the bending of the roll is carried out by means of a disk attached to the axle journal and by means of hydraulic loading elements acting upon said disk.
  • FIG. 15 is a schematic illustration of an embodiment of the roll in accordance with the invention in which glide bearings are employed in the interior of the roll mantle and in which the bending mechanism based on hydraulics is connected with the glide bearings.
  • Fig. 1 is an illustration of principle, in which the roll mantle 11 is bent by means of torques M ⁇ M ⁇ applied to both ends of the roll mantle 11.
  • the magnitude of the torque M j can be different from the magnitude of the torque M 2 , in which connection the running of the web proceeding on the roll mantle 11 can be controlled in the axial direction of the roll.
  • Fig. 2 shows an embodiment of the roll in accordance with the invention.
  • the roll consists of a continuous tubular roll mantle 11 of a composite material, which mantle has been fitted to revolve on the axle journals 12.
  • the first support sleeves 13 have been fitted, on which sleeves the roll mantle 11 itself has again been mounted.
  • the roll mantle 11 has been mounted on axle journals 12 by the intermediate of said first support sleeves 13 by means of bearings 14, 15.
  • the bearings 14, 15 have been installed at a distance from one another in the axial X— X direction of the roll, and, thus, the bearings form a pair of bearings.
  • the axle journals 12 consist of three parts 12a, 12b, 12c, all of which have different diameters.
  • the inner part 12a which extends into the interior of the end area of the roll mantle 11 , has the largest diameter D j
  • the following middle part 12b which is directed outwards from the end of the roll mantle 11 , has a slightly smaller diameter D 2
  • the outer part 12c which follows after the middle part 12b, has again a somewhat smaller diameter D 3 than the middle part 12b.
  • the axle journals 12 can, of course, be physically composed of the same piece, in which case said parts 12a, 12b, 12c have been formed, for example, by turning on a lathe.
  • a projection 16 which extends around the circumference of the axle journal and which forms an articulation member.
  • a second support sleeve 17 Onto the outer part 12c of the axle journal and partly onto the middle part 12b, a second support sleeve 17 has been fitted. This second support sleeve 17 extends beyond the projection 16 provided on the middle part 12b of the axle journal 12, and the inner diameter of the second support sleeve 17 is substantially equal to the outer diameter of the projection 16.
  • the second support sleeve 17 has been fixed to the frame R of the machine by means of two fastening members 18, 19.
  • the first fastening member 18 is placed at the projection 16, and the second fastening member 19 is placed at a distance from the outer end of the outer part 12c of the axle journal 12 and of the second support sleeve 17.
  • bending of the roll into curve form takes place by means of a bending mechanism 30 acting upon the outer end of the outer part 12c of the axle journal 12.
  • the bending mechanism 30 consists of a screw member 30 extending through the end of the second support sleeve 17 and through the outer end of the outer part 12c of the axle journal 12.
  • the screw member 30 is provided with an outer threading extending substantially through the second support sleeve 17, and the bore which extends through the outer part 12c of the axle journal 12 and which receives the screw member 30 is provided with a corresponding inner threading.
  • the second support sleeve 17 can be rotated in the direction of its circumference.
  • the screw member 30 and so also the axle journal 12 are rotated correspondingly.
  • the desired curve form is regulated for the roll mantle 11
  • the direction of the curve form of the roll mantle 11 is regulated in the direction of the circumference of the roll mantle 11.
  • the second support sleeve 17 has been mounted in the first 18 and the second 19 fastening member so that it cannot be rotated in relation to the fastening members 18,19 in any other way except by the effect of the regulation device 40.
  • the first fastening member 18 is provided with a first bearing member 20, which permits rotation and a slight axial movement of the second support sleeve 17.
  • the second fastening member 19 is provided with a corresponding second bearing member 21, which permits a slight axial movement of the second support sleeve 17.
  • This second bearing member 21 is locked with the support sleeve 17 so that the support sleeve 17 cannot be rotated in relation to the second bearing member 21 in the direction of the circumference.
  • the second bearing member 21 is coupled by means of an intermediate member 22 with the regulation device 40.
  • the regulation device 40 acts upon the second support sleeve 17, in which connection the second support sleeve 17 revolves in the direction of the circumference by the effect of the regulation device 40.
  • Fig. 3 shows an embodiment in which the screw member 30 that bends the roll mantle into a curve form is placed between the first fastening member 18 and the end of the roll mantle 11, and not after the second fastening member 19 as is shown in the embodiment of Fig. 2.
  • the parts 12b and 12c of the axle journal 12 change positions here, and the articulation point 16 is placed at the second fastening member 19.
  • Fig. 4 shows an embodiment which differs from the embodiment of Fig. 2 in respect of the fastening members 18, 19.
  • two fully separate fastening members 18,19 have been used, by whose means the second support sleeve 17 fitted on the axle journals 12 has been attached to the frame R of the machine.
  • a fastening flange construction is used in which there are two fastening members 18,19, which have a common lower part 90, which is attached to the frame R of the machine.
  • the second support sleeve 17 is still attached to the flange construction by means of two fastening points, which flange is also possible to think that the top portion of the fastening flange construction is made of one piece.
  • Fig. 5 shows an embodiment which differs from the embodiment shown in Fig. 2 in respect of the roll bending mechanism.
  • the roll bending mechanism consists of a screw member 60 parallel to the axis X— X of the roll, provided with an outer threading, and placed at the outer end of the second support sleeve 17.
  • the screw member 60 has been fitted in a fastening member 61 , which is fixed to the inner face of the second support sleeve 17 at its outer end and which is provided with a bore with an inside threading that receives the screw member 60 and that is parallel to the axis X— X of the roll.
  • the inner end of the screw member 60 is placed against the end face of a first wedge member 70.
  • the first wedge member 70 moves substantially parallel to the axis X— X of the roll on the inner face of the second support sleeve 17 by the effect of the screw member 60, but it has been locked against the inner face of the second support sleeve 17 to prevent radial movement.
  • the wedge face of this first wedge member 70 is again placed against the wedge face of the wedge member 71 attached to the outer part 12c of one of the axle journals 12.
  • Fig. 6 shows an embodiment which differs from the embodiments shown in Figs. 2...5 in respect of the bending mechanism.
  • a hydraulic or pneumatic cylinder or a stepping motor is used as the bending mechanism 100.
  • the rod 101 of the cylinder or of the stepping motor has been attached to an extension 12d provided on the axle journal 12, and the cylinder or the motor has been attached to the second support sleeve 17.
  • vertical movement of the rod 101 produces bending of the axle journal 12.
  • Fig. 7 is a schematic illustration of an embodiment of the roll in accordance with the invention, in which embodiment it is a difference as compared with the embodiments shown in Figs. 2...6 that the bearings of rotation of the roll are now placed outside the roll mantle 11.
  • the axle journal 12 has been attached to the end member 52 of the roll, which end member is fixed to the roll mantle 11, in which case the axle journal 12 revolves along with the roll mantle 11.
  • the axle journal 12 has been mounted revolving on a first support sleeve 50 by means of bearings 14,15.
  • the axle journal 12 is of substantially uniform thickness at least in respect of its portion between said bearings 14, 15.
  • the first support sleeve 50 is surrounded by a second support sleeve 51 , which has been attached to the frame R of the machine by means of fastening members 18,19, which are placed at said bearings 14,15 in the direction of the axis X— X of the roll.
  • a thicker portion 51a which extends across the first fastening member 18 in the direction of the axis X— X of the roll.
  • the inner diameter of the second support sleeve 51 is smaller than the inner diameter of the extension part 51b following after the thicker portion 51a.
  • an empty space 53 remains, in which the outer end of the first support sleeve 50 can move in the radial direction.
  • the thicker portion 51a of the second support sleeve 51 forms an articulation member of the first support sleeve 50, on whose support a little movement between the first support sleeve 50 and the second support sleeve 51 in the direction of the axis X— X of the roll is possible.
  • the bending mechanism 80 also comprises a screw member 80 installed outside the second fastening member 19, which screw member extends both through the first support sleeve 50 and through the second support sleeve 51.
  • the screw member 80 does not extend through the axle journal 12, which terminates at the second support bearing 15 before the screw member 80.
  • the screw member 80 is provided with an outer threading substantially in the portions that pass through the first 50 and the second 51 support sleeves.
  • first fastening members 81,82 resting against the inner face of the first support sleeve 50 and attached to the screw member 80, for example, by means of cotter pins.
  • second fastening members 83, 84 have been attached, which are provided with bores with inside threadings that receive the screw member 80.
  • bending of the axle journal 12 of the roll is produced so that the outer end of the first support sleeve 50 is displaced by means of the screw member 80 in relation to the second support sleeve 51.
  • the centre point of the second outer bearing 15 is displaced in relation to the central axis X— X of the roll, in which case the axle journal 12 is bent, and the roll mantle 11 is also bent.
  • Fig. 8 shows an embodiment which differs from the embodiment shown in Fig. 7 in respect of the roll bending mechanism.
  • a bending mechanism as described in the embodiment shown in Fig. 5 is used.
  • the screw member 60 has been fitted in a fastening member 61, which has been attached to the inner face of the second support sleeve 51 at its outer end and which is provided with an inside threading that receives the screw member 60.
  • the first support sleeve 50 is slightly shorter than the second support sleeve 51.
  • the second wedge member 71 has been attached to the outer face of the first support sleeve 50, in which case, being controlled by the screw member 60, the wedge members 70,71 bend the first support sleeve 50.
  • Fig. 9 shows an embodiment which differs from the embodiments shown in Figs. 7 and 8 in respect of the roll bending mechanism.
  • a hydraulic or pneumatic cylinder or a stepping motor is used as the bending mechanism 100.
  • the rod 101 of the cylinder or stepping motor has been attached to the first support sleeve, and the cylinder or stepping motor has been attached to the second support sleeve.
  • vertical movement of the rod 101 produces bending of the axle journal 12.
  • Fig. 10 shows an embodiment of the present invention, in which the bending takes place by means of two bending means 120, 130 in two planes perpendicular to one another.
  • the bending means 120,130 have been attached from one end to a substan- tially L-section support beam 110, which has again been attached to the frame R of the machine.
  • the opposite ends of the bending means 120,130 have been attached to a flange 113 that surrounds the second bearing 15.
  • the first bending device 120 displaces the axle journal 12 in the vertical plane Y
  • the second bending device 130 displaces the axle journal 12 in the horizontal plane X.
  • the desired curve form of the roll can be regulated, e.g. , by means of the first bending device 120, and the desired angular position of the curve form of the roll can be regulated by means of the second bending device 130.
  • the bending means 120,130 shown in Fig. 10 consist of a nut member 123, 133 provided with inside threading, a first pin 121 , 131 , which is fixed to a flange 113 and which is provided with an outside threading, being fitted to one end of said nut member, an a second pin 122,132, which is fixed to a sledge 124,134 moving on the beam 110 and which is provided with an outside threading, being fitted to the opposite end of said nut member 123,133.
  • the axle journal 12 and, thereby, the roll mantle 11 can be bent in the X— Y-planes.
  • the sledge 124 which is fitted on the horizontal part of the beam 110, can move in the X-plane on support of the wheels 125, but it has been locked in respect of the beam 110 against movement in the Y-plane.
  • the sledge 134 fitted on the vertical part of the beam 110 can move in the Y-plane on support of the wheels 135, but it has been locked in respect of the beam 110 against movement taking place in the X- plane.
  • the wheels 125,135 of the sledges 124, 134 revolve on guide rails or equivalent that have been formed on the beam 110.
  • the wheel arrangement 125,135 is just one example of a mode in which the mounting of the sledges 124,134 on the beam 110 can be accomplished so that movement of the sledge 124 in the direction X and movement of the sledge 134 in the direction Y are permitted.
  • a nut-pin solution herein it is also possible to employ, for example, a hydraulic or pneumatic cylinder or a stepping motor.
  • Fig. 11 shows a variation of the embodiment shown in Fig. 10, in which the journal- ling and bending of the axle journal 12 are carried out by means of at least one magnetic bearing.
  • At least one of the bearings 14,15 is a magnetic bearing 15, by whose means the axle journal 12 of the roll and, thereby, the roll mantle 11 can be bent.
  • the axle journal 12 can be displaced eccentrically in relation to the housing.
  • the magnetic bearing 15 permits bending of the roll axle 12 and, thus, also of the roll mantle 11 to the desired curve form in the X— Y-planes and regulating of the angular position of the arc of the roll mantle 11 formed by bending to the desired position.
  • both bearings 14, 15 can also be magnetic bearings.
  • Fig. 12 shows a second variation of the embodiment shown in Fig. 10, in which the bending of the axle journal 12 and the angular position of the bending are regulated by means of a magnet 260.
  • the magnet 260 consists of a number of sector-shaped parts, and the magnetic flux of each sector can be regulated separately.
  • Fig. 13 shows a third variation of the embodiment shown in Fig. 10, in which the bending of the axle journal 12 is carried out by means of a nut member 153, and the angular position of the bending is regulated by means of a rack-gearwheel device 160, 150.
  • the flange 113 which surrounds the second bearing 15 has been attached to the gearwheel device 150 by means of the nut member 153.
  • the nut member 153 provided with an inside threading, is similar to the nut members 123,133 shown in Fig. 11, and to one of its ends a pin 151 projecting from the bearing flange 113 and provided with outside threading has been fitted, and to its opposite end a pin 152 projecting from the gearwheel device 150 and provided with outside threading has been fitted.
  • the gearwheel device 150 comprises a gearwheel 154 mounted on the gearwheel device 150 by means of its shaft 155.
  • the shaft 155 of the gearwheel 154 projects from the gearwheel device 150, and the projecting portion is preferably of quadrangular section, in which case it can be rotated, for example, by means of a lever tool suitable for the purpose.
  • the rack device 160 comprises a rack 161 substantially shaped as an arc of a circle, along which the gearwheel 154 runs.
  • the rack device 160 further comprises a guide part 162, which glides in the guide groove 156 of the gearwheel device 150.
  • the rack device 160 is attached to the beam 140, which is again attached to the frame R of the machine.
  • the gearwheel 154 of the gearwheel device 150 it is possible to regulate the angular position of the curve form of the roll mantle 11.
  • the gearwheel device 150 can be locked in the desired angular position on the rack 161 by means of a screw locking device 157, which tightens the sledge 150 against the rack 161.
  • Fig. 14 shows an embodiment in accordance with the invention, in which the bending of the axle journal 12 is carried out by means of a disk member 180 attached to the axle journal 12.
  • the fastening flange construction 170 attached to the frame R of the machine consists of two vertical walls of substantially rectangular shape placed at an axial distance from one another, i.e. a front wall 171 and a rear wall 172.
  • the bottom edge and the top edge of the front wall 171 and of the rear wall 172 have been interconnected by means of a substantially rectangular horizontal bottom wall 173 and top wall 174.
  • the side edges of the front wall 171 and the rear wall 172 have been interconnected by means of a substantially rectangu- lar vertical first side wall 175 and second side wall 176.
  • the walls 171,172, 173, 174,175, 176 define a hollow cavity space 190 in their interior, in which space the disk 180 attached to the axle journal 12 revolves along with the axle journal 12.
  • the axle journal 12 extends through the hole 177 provided in the front wall 171 of the fastening flange construction 170 and through the hole 178 provided in the rear wall 172 and has been mounted revolvingly by means of a bearing 15 in the rear wall 172.
  • the diameter of the hole provided in the front wall is larger than the outer diameter of the axle journal 12.
  • thin capillary ducts (not shown in the figure) pass through the pistons 190a, 191a into lubrication pockets 220,221 of the loading elements 190, 191.
  • loading elements 190,191 on each face 180a, 180b of the disk 180, i.e. a total of eight elements.
  • the loading elements 190, 191 are placed at the intersection points between the circumference of a circle drawn at the centre of the axle journal 12, the X-axis, and the Y-axis.
  • the axle journal 12 and, thereby, the roll mantle 11 are bent by means of the disk 180 attached to the axle journal 12 and by means of the hydraulic loading elements 190, 191 acting upon said disk.
  • the roll mantle 11 can be bent to the desired curve form and to the desired angular position.
  • Fig. 15 shows an embodiment which differs from the embodiments shown in the preceding figures in respect of the bending mechanism, the bearing arrangement, and the axle journal.
  • the axle journal 12 is of substantially uniform thickness over its entire length, and it is not bent.
  • the journalling of the axle journal 12 in a first support sleeve 13 fitted inside the roll mantle 11 has been arranged by means of hydrostatic or hydrodynamic glide bearings 70,71, on whose support the roll mantle 11 revolves in relation to the axle journals 12.
  • the glide bearings 70,71 are placed at a distance from one another in the direction of the axis X— X of the roll.
  • a duct 72 parallel to the axis X— X of the axle journal has been made into the axle journal 12, together with radial ducts 73,74 at the locations of the glide bearings.
  • the first bearing 70 which operates exclusively as a glide bearing, has been attached to the axle journal 12 by means of an articulated joint so that its central axis Y— Y can turn in relation to the radius of the axle journal 12.
  • the second bearing 71 has been provided with a possibility to displace the bearing in the direction of the radius of the axle journal 12.
  • This second bearing 71 has been attached to the axle journal 12 so that it can move in the direction of the radius of the axle journal 12, and at the same time its central axis Y-Y can turn in relation to the radius of the axle journal 12.
  • two separately controllable hydraulic feeds 74a, 74b are passed into this second bearing 71 .
  • Figs. 10...13 it is shown that the bending is carried out at the second, outer support point, in relation to the end 52 of the roll, but a reversed situation is also possible.
  • the bending mechanism is placed at the inner support point, and the outer support point is fixed.
  • the bending of the roll mantle 11 takes place by means of forced shifting by means of a screw 30,80, a screw-nut assembly 120, 130, 151...153, a wedge 70, or equivalent.
  • the screw 30, 80, the screw-nut assembly 120, 130, 151...153, the wedge 70, or equivalent binds the axle journal 12 with the support point rigidly, in which case the roll is, so to say, rigidly supported in the sense of vibration.
  • the bending of the roll mantle 11 takes place by means of hydraulics, pneumatics, or by means of a stepping motor 100,101,190,250,260 in which case the roll is, so to say, freely supported or articulation-supported in the sense of vibration.
  • a hydraulic medium and a pneumatic medium usually yield to some extent, in which case the support is provided with a slight extent of resilience.
  • the bending of the roll mantle 11 takes place directly from the roll mantle 11 from inside the support point of the axle journal 12.
  • the bearings 70,71 bind the roll with the first support sleeve 13 rigidly.
  • the roll is rigidly supported in the sense of vibration.
  • the lowest natural frequency of the roll becomes more than twice as high as compared with a freely supported roll.
  • the natural frequency of a roll becomes higher, it is possible to use smaller roll diameters, in which case the forces transferred from the bending to the frame of the machine are reduced and the cost of manufacture of the roll becomes lower.

Landscapes

  • General Engineering & Computer Science (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Paper (AREA)
  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Laminated Bodies (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Nonwoven Fabrics (AREA)
  • Professional, Industrial, Or Sporting Protective Garments (AREA)
  • Orthopedics, Nursing, And Contraception (AREA)

Abstract

L'invention concerne un cylindre pour une matière de type bande qui peut être cintré. Le cylindre comporte une enveloppe (11) de cylindre tubulaire continue, constituée d'une matière composite; ainsi que des fusées (12) d'essieu connectées à chaque extrémité du enveloppe (11) de cylindre. Les fusées (12) d'essieu sont connectées par au moins un point d'appui à une construction (18, 19) de bride de fixation montée sur le cadre (R) de la machine. Le cylindre comporte en outre un mécanisme (30) de cintrage qui permet de cintrer les fusées (12) d'essieu, et de ce fait l'enveloppe (11) de cylindre, en forme d'arc; et un dispositif (40) de réglage permettant de régler la position angulaire de l'arc de cylindre.
EP98938719A 1997-08-19 1998-08-11 Cylindre pour matiere de type bande pouvant etre cintre Expired - Lifetime EP1003980B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
FI973388 1997-08-19
FI973388A FI102560B1 (fi) 1997-08-19 1997-08-19 Taivutettava tela rainamaista materiaalia varten
FI980071A FI103071B (fi) 1997-08-19 1998-01-15 Taivutettava tela rainamaista materiaalia varten
FI980071 1998-01-15
PCT/FI1998/000623 WO1999009329A1 (fr) 1997-08-19 1998-08-11 Cylindre pour matiere de type bande pouvant etre cintre

Publications (2)

Publication Number Publication Date
EP1003980A1 true EP1003980A1 (fr) 2000-05-31
EP1003980B1 EP1003980B1 (fr) 2007-10-03

Family

ID=26160427

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98938719A Expired - Lifetime EP1003980B1 (fr) 1997-08-19 1998-08-11 Cylindre pour matiere de type bande pouvant etre cintre

Country Status (9)

Country Link
US (1) US6524227B1 (fr)
EP (1) EP1003980B1 (fr)
JP (1) JP4077153B2 (fr)
AT (1) ATE374889T1 (fr)
AU (1) AU8733698A (fr)
CA (1) CA2301276C (fr)
DE (1) DE69838504T2 (fr)
FI (1) FI103071B (fr)
WO (1) WO1999009329A1 (fr)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI105116B (fi) 1998-11-30 2000-06-15 Valmet Corp Valmet Corp Paperi- tai kartonkikoneessa käytettävä taivutettava palkki
FI106741B (fi) 2000-03-16 2001-03-30 Metso Paper Inc Komposiittivaippainen taivutettava tela
DE20006302U1 (de) * 2000-04-06 2001-10-25 Band-Zink-GmbH, 40764 Langenfeld Beschichtungsvorrichtung
DE20309301U1 (de) * 2003-06-13 2003-08-28 Stowe Woodward AG, 33758 Schloß Holte-Stukenbrock Breitstreckwalze
DE10335758C5 (de) * 2003-08-05 2015-12-03 Manroland Web Systems Gmbh Verfahren und Druckwerk zur Beeinflussung der lateralen Bahnspreizung insbesondere an Rotationsdruckmaschinen
DE10340569A1 (de) * 2003-09-01 2005-04-07 Koenig & Bauer Ag Verfahren zur Reduktion von Passerfehlern auf einer in einer bahnverarbeitenden Vorrichtung und ein Druckwerk
DE10341119A1 (de) * 2003-09-05 2005-03-31 Voith Paper Patent Gmbh Breitstreckwalze
DE202004021651U1 (de) * 2004-05-29 2009-10-08 Voith Patent Gmbh Drehteil
FI116745B (fi) * 2004-07-13 2006-02-15 Pr Rolls Oy Taivutettava tela
FI117640B (fi) * 2004-07-28 2006-12-29 Metso Paper Inc Johtotela rainanmuodostuskonetta varten ja menetelmät vastaavan johtotelan valmistamiseksi ja käyttämiseksi
FI117646B (fi) 2004-10-04 2006-12-29 Metso Paper Inc Tela
DE102005044956A1 (de) * 2005-09-20 2007-03-22 Voith Patent Gmbh Breitstreckwalze
AU2006225177B2 (en) * 2006-01-12 2009-05-21 Innovative Design Co Pty Ltd Container closure
FR2919511B1 (fr) * 2007-07-30 2010-01-29 Snecma Propulsion Solide Rouleau composite thermostructural
FI123493B (fi) * 2009-08-04 2013-05-31 Finbow Oy Kaarevan telan kiinnityselin sekä järjestely ja menetelmä kaarevan telan värähtelyn hallintaan
DE102009048074A1 (de) 2009-10-01 2011-04-07 Brückner Maschinenbau GmbH & Co. KG Reckwalze sowie zugehöriges Längsreckwerk oder -stufe
JP6163805B2 (ja) * 2013-03-15 2017-07-19 株式会社リコー 画像形成装置
KR20230064231A (ko) * 2021-11-03 2023-05-10 주식회사 엘지에너지솔루션 자재 지지용 롤러

Family Cites Families (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1848547A (en) * 1932-03-08 b scharnberg
US2676387A (en) * 1951-07-11 1954-04-27 Downingtown Mfg Co Mounting for smoothing press rolls
US2771658A (en) * 1953-08-03 1956-11-27 Hunter James Machine Co Roll for expanding and contracting textiles
US2955897A (en) * 1956-10-01 1960-10-11 Kidde Textile Machinery Corp Warping machine
US2898662A (en) * 1957-05-17 1959-08-11 Mount Hope Machinery Ltd Expanding and contracting rolls
US2960749A (en) * 1958-08-20 1960-11-22 Mount Hope Machinery Ltd Expanding and contracting rolls
US3085503A (en) * 1960-11-16 1963-04-16 Black Clawson Co Paper machinery
US3168435A (en) * 1960-11-25 1965-02-02 Beloit Corp Method and means for mounting, driving and supporting rolls for endless moving bands
US3094771A (en) * 1961-06-13 1963-06-25 Mount Hope Machinery Ltd Table roll with means for removing longitudinal curvature
US3182787A (en) * 1963-10-15 1965-05-11 Joy Mfg Co Conveyor device
US3347157A (en) * 1965-04-30 1967-10-17 Farrel Corp Roll structures and method
US3373588A (en) * 1965-08-17 1968-03-19 United Eng Foundry Co Crown control for rolling mill
US3443295A (en) * 1966-02-04 1969-05-13 Beloit Corp Table roll
US3438100A (en) * 1966-05-06 1969-04-15 Beloit Eastern Corp Adjustable shot roll
US3448683A (en) * 1966-12-16 1969-06-10 Adamson United Co Calender with removable bearing pressure mechanism
US3537665A (en) * 1968-10-18 1970-11-03 United Eng Foundry Co Replaceable mandrel for tension reel
US3604087A (en) * 1970-03-13 1971-09-14 Beloit Corp Antideflection roll
AT311167B (de) * 1970-07-08 1973-11-12 Joseph Eck & Soehne Kg Knickwalze, insbesondere für Papierkalander
DE2042001A1 (de) * 1970-08-25 1972-04-27 Kleinewefers Ind Co Gmbh Leitwalze an Kalandern
US4011938A (en) * 1975-09-08 1977-03-15 Kain Arthur F Suspension idler
CH611990A5 (fr) * 1977-01-17 1979-06-29 Sulzer Ag
US4180296A (en) * 1978-01-06 1979-12-25 Societe Europeenne De Propulsion Axial electromagnetic bearing for a shaft rotating at high speed
CA1109015A (fr) * 1979-02-20 1981-09-15 Ronald G. Dunk Mecanisme d'entrainement et de soutien de rouleaux en ceramique, et mode d'emploi connexe
CH648238A5 (de) * 1979-10-09 1985-03-15 Roland Man Druckmasch Vorrichtung zum durchbiegen einer druckwalze einer rotationsdruckmaschine.
US4364158A (en) * 1980-09-02 1982-12-21 Usm Corporation Roll bending apparatus
FI67675C (fi) * 1980-09-04 1985-05-10 Frankenthal Ag Albert Cylinder foer banformiga material bearbetande maskiner
FI811720A0 (fi) * 1981-06-03 1981-06-03 Waertsilae Oy Ab Valskonstruktion
IT1155103B (it) * 1982-03-03 1987-01-21 Componenti Grafici Srl Cilindro di pressione con asse a configurazione variabile
DE3826980A1 (de) * 1987-08-13 1989-02-23 Barmag Barmer Maschf Fliegend gelagerte streckgalette
US5061533A (en) * 1988-10-11 1991-10-29 Mitsubishi Rayon Company Ltd. Roll formed of carbon fiber composite material
DE3912303C2 (de) * 1989-04-14 1994-08-04 Troester Maschf Paul Kalander für die Herstellung von Dichtungsplatten
CH680151A5 (fr) * 1989-11-09 1992-06-30 Escher Wyss Ag
FI87485C (fi) * 1991-01-07 1993-01-11 Valmet Paper Machinery Inc Boejningsreglerbar vals
JPH08244108A (ja) * 1995-03-13 1996-09-24 Toshiba Mach Co Ltd シート等の成形用のロールベンディング装置
DE29508422U1 (de) * 1995-05-20 1995-08-10 Voith Sulzer Papiermaschinen GmbH, 89522 Heidenheim Walze mit Schwingungsdämpfer
JPH08326755A (ja) * 1995-06-05 1996-12-10 Hitachi Ltd 軸受ユニット
DE19616802A1 (de) * 1996-04-26 1997-10-30 Voith Sulzer Papiermasch Gmbh Durchbiegungsausgleichswalze
US5739609A (en) * 1997-04-09 1998-04-14 Koyo Seiko Co., Ltd. Magnetic bearing apparatus

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9909329A1 *

Also Published As

Publication number Publication date
FI980071A (fi) 1999-02-20
WO1999009329A1 (fr) 1999-02-25
FI980071A0 (fi) 1998-01-15
CA2301276A1 (fr) 1999-02-25
DE69838504D1 (de) 2007-11-15
EP1003980B1 (fr) 2007-10-03
AU8733698A (en) 1999-03-08
US6524227B1 (en) 2003-02-25
DE69838504T2 (de) 2008-04-24
FI103071B1 (fi) 1999-04-15
FI103071B (fi) 1999-04-15
ATE374889T1 (de) 2007-10-15
JP4077153B2 (ja) 2008-04-16
JP2001515192A (ja) 2001-09-18
CA2301276C (fr) 2007-11-27

Similar Documents

Publication Publication Date Title
CA2301276C (fr) Cylindre pour matiere de type bande pouvant etre cintre
US7867155B2 (en) Expander roller
US7824320B2 (en) Expander roller
JP3056609U (ja) 変形制御ロール
FI121825B (fi) Levitystela
CA1275281C (fr) Dispositif fronceur a rouleaux
CA2623185A1 (fr) Rouleau deplisseur
CN100504088C (zh) 辊
CA2177797C (fr) Agencement d'entrainement pour cylindre d'enduction
FI115554B (fi) Laitteisto paperi-, kartonki- tai jälkikäsittelykoneen telan tukemiseksi sekä menetelmä telan taipuman ohjaamiseksi
CA2340870C (fr) Cylindre pouvant etre replie avec une chemise en composite
EP0932723B1 (fr) Rouleau de guidage d'une bande mobile
FI57471B (fi) Vals med reglerbar nedboejning
EP0937005B1 (fr) Rouleau guide debiteur, rouleau deplisseur ou equivalent, pour un materiau sous forme de bande
FI102560B (fi) Taivutettava tela rainamaista materiaalia varten
US20020132712A1 (en) Self-adjusting deflection controlled roll
FI105116B (fi) Paperi- tai kartonkikoneessa käytettävä taivutettava palkki
EP0786032B1 (fr) Appareil pour positionner dans le sens axial la virole de cylindre dans un cylindre a deviation controlee charge de maniere hydrostatique
CN1302933A (zh) 轧辊组件和轧辊
US3418703A (en) Antideflection roll with non-rotating beam and lever supports
WO1998058182A1 (fr) Procede de production, et structure pour corps de forme allonge resistant a la flexion
JPH09508676A (ja) セルフローディング式たわみ制御ロール
JP3095650B2 (ja) 軸受メタル可変位相型軸受
US5860322A (en) Drive mechanism of a suction roll including a spur wheel gear and an outward mounting portion for a stationary suction box
FI121017B (fi) Palkkirakenne paperin- ja kartonginvalmistuskoneisiin sekä menetelmä sen muodostamiseksi

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20000218

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT DE FR GB IT SE

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: METSO PAPER, INC.

17Q First examination report despatched

Effective date: 20031219

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT DE FR GB IT SE

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 69838504

Country of ref document: DE

Date of ref document: 20071115

Kind code of ref document: P

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080103

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20080704

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20110824

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20120821

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20120906

Year of fee payment: 15

Ref country code: DE

Payment date: 20120822

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20120813

Year of fee payment: 15

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120811

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 374889

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130811

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20130811

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140301

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20140430

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 69838504

Country of ref document: DE

Effective date: 20140301

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130811

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130811

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130902